US4746076A - Winder device - Google Patents

Winder device Download PDF

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Publication number
US4746076A
US4746076A US06/927,261 US92726186A US4746076A US 4746076 A US4746076 A US 4746076A US 92726186 A US92726186 A US 92726186A US 4746076 A US4746076 A US 4746076A
Authority
US
United States
Prior art keywords
support
roll
winder
drum
rotatable
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US06/927,261
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English (en)
Inventor
Kauko Tomma
Seppo Saukkonen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valmet Paper Machinery Inc
Original Assignee
Wartsila Oy AB
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Filing date
Publication date
Application filed by Wartsila Oy AB filed Critical Wartsila Oy AB
Assigned to OY WARTSILA AB reassignment OY WARTSILA AB ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: SAUKKONEN, SEPPO, TOMMA, KAUKO
Application granted granted Critical
Publication of US4746076A publication Critical patent/US4746076A/en
Assigned to VALMET PAPER MACHINERY INC. reassignment VALMET PAPER MACHINERY INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: OY WARTSILA AB
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H18/00—Winding webs
    • B65H18/08—Web-winding mechanisms
    • B65H18/14—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web
    • B65H18/22—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web by friction band
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H18/00—Winding webs
    • B65H18/08—Web-winding mechanisms
    • B65H18/14—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web
    • B65H18/20—Mechanisms in which power is applied to web roll, e.g. to effect continuous advancement of web the web roll being supported on two parallel rollers at least one of which is driven
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/40—Shafts, cylinders, drums, spindles
    • B65H2404/43—Rider roll construction

Definitions

  • the invention relates to a winder device.
  • Typical for modern winders of this kind is that paper webs are wound at a web running speed of more than 2000 m/min.
  • the line or nip pressure between the roll and its support drum should be at least about 1 . . . 4 kN/m, depending on the paper grade to be wound.
  • a small-sized support drum If a small-sized support drum is used, the nip pressure tolerated by the roll will be exceeded, in particular during the final phase of winding a big roll. This is because a small support drum provides a very narrow support area giving a high contact pressure at a given roll weight. Further, local pressure peaks may occur due to uneven paper web thickness in the web transverse direction. Attempts have been made to reduce the support pressure by increasing the dimension of the support drum, but this measure increases the manufacturing costs and operational expenses due to the increased inertia of the drum. Thus, an increase of the drum diameter is profitable only up to a certain limit. This limit has already been reached in conventional support drum winders.
  • a support drum generates, in the supported roll, radial depressions and sometimes also circumferential dislocations of the roll layers. This may cause ruptures and wrinkles in the web. Decreased nip pressure reduces the generation of nip pressure dependent roll defects.
  • Patent Specification EP No. 157062 corresponding to U.S. patent application Ser. No. 529512 of 1983, discloses a soft-surface support drum. Such a drum decreases the nip pressure, but gives rise to dynamic shaping problems because two yielding surfaces are brought together in a nip, which results in stability problems and heat generation.
  • the weight of a paper roll may also entirely or partially be taken up by central shaft support means. This makes it possible to effectively control the roll density and the nip pressure throughout the entire winding process, and thus, winding faults caused by excess support nip pressure can to a great extent be eliminated, see Patent Specification GB No. 2142909.
  • U.S. Pat. No. 4,143,828 shows a central shaft support system having also belt support means. This winder is a Pope-type reel-up winder using a rigid central shaft. Practically the entire support load is taken up by the shaft.
  • the object of the invention is to create a device, in which excess nip pressure caused by increasing roll weight is eliminated while maintaining the advantages of conventional support drum winding. Another object is to create an arrangement, in which the winding nip pressure is easily controllable and the load caused by the roll weight is taken up by a large support surface.
  • Patent Specification DE No. 2908294 discloses a winder with some features similar to the features of the invention.
  • This known design uses two stationary drums arranged in vertical alignment and a third movable drum, which is operated to carry out several functions: the function of a rider roll, of a support drum and of a control member determining the tension of a support belt.
  • the increasing paper roll diameter determines the position of the movable drum, and this means that the rider roll function of the movable drum is eliminated as the winding process advances.
  • the entire support picture will change and the paper roll will be supported practically only by the lower one of the stationary drums and by the movable drum. This change is difficult to control accurately, which means that there is a considerable risk of uncontrolled excess nip pressures occurring.
  • a preferred embodiment of the invention is a winder device for winding a moving web, such as a paper or cardboard web, to form a roll of considerable weight.
  • the roll is carried by support members which give the roll peripheral support.
  • the support members comprise a movable support web device and a rotatable winder drum which is spaced from the support web device about the periphery of the roll.
  • the support members form the main support for the roll.
  • the support web device includes a support web having a portion between two rotatable support elements, which support web portion has a surface of contact with the roll giving the roll support. The surface of contact is continuously enlarged when the roll grows, in order to eliminate the risk of roll damage due to excess support pressure when winding heavy rolls.
  • the web is conducted to the roll about the periphery of the winder drum and through the space between the winder drum and the support web device.
  • the hardness of a wound roll is determined by the nip pressure which is dependent on the roll weight. These factors are controlled by determining the relative position of the paper roll, the winder drum and the other support members. If a rider roll is used, its load is accurately controlled as well.
  • the advantages of a conventional support drum winder are achieved by keeping the paper roll at or above the level of the center of the winder drum.
  • the supporting properties of the support web are adjusted by controlling the web tension and the relative position of the web support drums.
  • the supporting portion of the support web extends during a phase of the winding from a nip between the paper roll and the first support drum towards the other support drum. Thereafter, during another winding phase, the support portion of the web extends into or very close to both nips between the roll and the support drums, thereby supporting a big roll over a considerable portion of its circumference.
  • the distribution of the support forces can also be adjusted by altering, in relation to the increase in roll diameter, the position of the nip between the roll and the winder drum.
  • the support force distribution is also influenced because the loading direction of the rider roll, alters relatively to the drums of the winder because of the increasing diameter of the paper roll.
  • the shaft of the winder drum and the shaft of the first support drum define a reference plane and the second support drum is movable relative to this plane.
  • the angle between a line through the center of the support drums and the reference plane should be adjustable 45° upwards from the reference plane and the same angle downwards, or at least 15° downwards.
  • the reference plane should be adjustable about ⁇ 20° from its normal position. This can be done by adjusting the vertical position of either the winder drum or the first support drum.
  • the diameter of the winder drum should preferably be 3.5 to 1.5 times the diameter of the first support drum.
  • the support drums and the support web should take up at least half the weight of the roll already at a relatively early stage of the winding.
  • the roll diameter exceeds 300 mm preferably at least 60% of the support forces, eventually even 80% should be taken up by the web support arrangement.
  • the support forces include the weight of the roll and the vertical load component of the rider roll.
  • the position of the second support drum and the support web tension are adjusted so, that during an early winding phase the support contact portion of the support web increases continuously. Later, the roll is supported by the winder drum, by the two support drums and by the support web. The tension of the support web will be so adjusted that the roll weight received by the support web between the support drums is at least mainly uniformly distributed.
  • the uniform load distribution should include, in the most favourable alternative, also the nips provided by the two support drums.
  • the support is thus extended over a surface which is at least ten times the nip support surface of a support drum in a conventional support drum winder.
  • the nip pressure acting on the roll can be reduced to only about 20%, and sometimes to even less than 10% of the nip pressure in a winder of the kind shown in U.S. Pat. No. 4,456,190.
  • the maximum pressure tolerated by a paper roll is about 4 to 12 times the support pressure in a device according to the invention.
  • the invention makes it possible to wind considerably bigger and heavier rolls than in conventional winders. In practice, it has been possible to wind rolls with a weight of about 3000 kg per meter axial roll length.
  • FIG. 1 is a schematical side view of an embodiment of invention
  • FIG. 2 is a portion of FIG. 1 shown on a larger scale
  • FIGS. 3A, 3B and 3C illustrate consecutive winding phases
  • FIGS. 4A, 4B and 4C visualize the support distribution in a roll in some typical support cases.
  • a running paper web 1 is wound on a core 3 to form a roll 2.
  • the roll rotates as shown by an arrow 40 and is supported by a winder drum 4 and a support web device 8.
  • the winder drum 4 is rotatably journalled and has a central shaft 5.
  • the support web device 8 comprises a stationary first support drum 10 and a movable second support roll 10a, both rotatably journalled at their respective center 23.
  • a support arm 18 turnable around a fixed point 23a carries the movable support roll 10a adjustable as shown by arrows 16 by turning support arm 18 around its fixed point 23a.
  • An endless support web 11 runs over the drums 10, 10a, 12 and 13. This web or belt may be composed by a number of belts running side by side.
  • Tension drum 13, movable as indicated by arrows 17, is carried by a movable lever 18a journalled at a fixed point 23b.
  • Winder drum 4 and support drum 10 define a reference plane 14 (FIG. 2).
  • operative members 19, 19a and 20, 20a There are hydraulic or pneumatic operative members 19, 19a and 20, 20a.
  • Members 19, 19a operate between a fixed frame element 9 and support arm 18 to adjust the position of drum 10a.
  • Members 20, 20a maintain the web tension by operating between lever 18a and support arm 18.
  • the operative members have pressure or force sensors 37, which through connections 38 transmit pressure or force information to a measuring and control device (not shown).
  • nips 24, 25 and 35 When the roll 2 reaches its maximum diameter, it is supported by three nips 24, 25 and 35. Between nips 24 and 25 support web 11 has a portion 26, which also works as a roll supporting element carrying a considerable portion of the load produced by the weight of roll 2 and by the load of rider roll 6, if any.
  • the load direction of rider roll 6 is indicated by reference numerals 27a-c.
  • FIG. 3A shows the start of the winding process.
  • the load 27a of rider roll 6 is always directed towards the center of the roll 2.
  • winder drum 4 and support drum 10 give support at nips 35 and 24, respectively.
  • roll 2 has become considerably bigger and a portion of its weight is received by support portion 26 of web 11.
  • the roll 2 presses web portion 26 downwards.
  • the tension of support web 11 is adjusted so that the pressure between roll 2 and the support web is as uniform as possible over the total contact area.
  • FIG. 3C shows the beginning of the final winding phase.
  • the load of roll 2 and of rider roll 6, if applied, is taken up by winder drum 4 and the entire portion 26 of support web 11 between support roll nips 24 and 25.
  • the angle 41 between reference plane 14 and the plane defined by the shafts of drums 10 and 10a is preferably between 0° . . . 45°, and the angle 42 between reference plane 14 and a horizontal line is 10° . . . 20°.
  • FIG. 4A shows a conventional support drum arrangement.
  • the entire support load of a support drum is transmitted in the form of a load peak 29 at the support nip 29a to a supported paper roll 2. This easily causes damage in roll 2, in particular, if the total weight of the roll exceeds 1.5 tons/meter.
  • FIG. 4B visualizes a support according to the invention.
  • Support web 11 follows the surface of roll 2, starting from nip 24 to nip 25. This means that the tension in support web 11 is not the best possible.
  • load peaks 30, 30a occur at nips 24 and 25. However, these peaks are very much smaller than the load peak in FIG. 4A and in most cases not even 50% of what they would be, if there were no support web 11 or no tension in the support web 11.
  • the arrangement shown in FIG. 4B is suitable for strong paper webs having a relatively low compressibility.
  • FIG. 4C visualizes what is considered to be the most favourable embodiment of the invention.
  • the tension of support web 11 is increased so that more of the support is provided by web portion 26 and less by nips 24 and 25.
  • the tension of support web 11, the relative position of drums 4, 10, 10a and the load of rider roll 6 are so controlled in relation to the increase of weight and diameter in roll 2, that when the diameter of roll 2 exceeds 500 mm, the load 31 is kept as uniform as possible.
  • the load variations within the support area should be maximum ⁇ 25%, preferably less than ⁇ 10%.
  • the pressure distribution might vary somewhat in the transverse direction of web 1 depending on profile variations in the paper web, variations in roll diameter, etc.
  • FIGS. 4B and 4C have been simplified so that the load distribution is symmetrical. Unsymmetrical load distribution does not change the general principles of the invention.
  • a further embodiment of the invention is, for instance, an arrangement, in which winder drum 4 is replaced by a support arrangement corresponding to support web device 8. Then roll 2 receives a double-sided belt support.
  • winder drum 4 is replaced by a support arrangement corresponding to support web device 8.
  • roll 2 receives a double-sided belt support.
  • support web 11 one may apply barrel-shaped drums, guide collars or cylinders commonly used for paper machine wires and felts.

Landscapes

  • Winding Of Webs (AREA)
  • Replacement Of Web Rolls (AREA)
  • Macromolecular Compounds Obtained By Forming Nitrogen-Containing Linkages In General (AREA)
US06/927,261 1985-11-20 1986-11-04 Winder device Expired - Lifetime US4746076A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI854571A FI74260C (fi) 1985-11-20 1985-11-20 Upprullningsanordning.
FI854571 1985-11-20

Publications (1)

Publication Number Publication Date
US4746076A true US4746076A (en) 1988-05-24

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Family Applications (1)

Application Number Title Priority Date Filing Date
US06/927,261 Expired - Lifetime US4746076A (en) 1985-11-20 1986-11-04 Winder device

Country Status (11)

Country Link
US (1) US4746076A (fi)
JP (1) JPH0694319B2 (fi)
AT (1) AT399855B (fi)
AU (1) AU581351B2 (fi)
CA (1) CA1264048A (fi)
DE (1) DE3639244C2 (fi)
FI (1) FI74260C (fi)
FR (1) FR2590244B1 (fi)
GB (1) GB2183223B (fi)
NO (1) NO162226C (fi)
SE (1) SE461585B (fi)

Cited By (36)

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Publication number Priority date Publication date Assignee Title
US4842209A (en) * 1987-05-20 1989-06-27 Valmet Paper Machinery Inc. Method and device in the winding of a web
US4901935A (en) * 1987-05-27 1990-02-20 Ferag Ag Apparatus for unwinding printed products wound in conjunction with a winding band in imbricated formation upon a winding core
US4921183A (en) * 1987-05-20 1990-05-01 Valmet Paper Machinery Inc. Method and device for the reeling of a web
US4927091A (en) * 1987-04-29 1990-05-22 Jagenberg Aktiengesellschaft Device for winding and unwinding a web of material
US5022597A (en) * 1989-09-27 1991-06-11 Krantz America, Inc. Sheet winding apparatus
US5067871A (en) * 1988-07-18 1991-11-26 Kone Oy Procedure for horizontal storage of paper rolls
US5150850A (en) * 1991-05-10 1992-09-29 Beloit Corporation Method for winding a traveling web on a belted two drum wound web roll winder
US5167376A (en) * 1989-12-07 1992-12-01 G.D. Societa' Per Azioni Device for removing adhesive tape from a reel of strip material
US5209418A (en) * 1985-04-24 1993-05-11 Alexander Machinery, Inc. Web unwinding apparatus and method
US5257748A (en) * 1989-09-27 1993-11-02 Krantz America, Inc. Sheet winding apparatus
US5732902A (en) * 1994-05-26 1998-03-31 Valmet Corporation Method and device in winding of a web
WO1999001363A1 (en) * 1997-07-03 1999-01-14 Valmet-Karlstad Ab Apparatus and method for winding paper
US5918830A (en) * 1997-02-13 1999-07-06 Valmet Corporation Reeling device and method in reeling of a paper web or equivalent
WO1999035070A1 (en) * 1997-12-22 1999-07-15 Valmet Corporation Pressure roller reel-up
US5938144A (en) * 1997-06-25 1999-08-17 Voith Sulzer Papiermaschinen Gmbh Winding machine
WO1999064335A1 (en) * 1998-06-10 1999-12-16 The Goodyear Tire And Rubber Company Surface winding on an a-frame winder
US6012673A (en) * 1997-08-12 2000-01-11 Voith Sulzer Finishing Gmbh Winding device and method
US6145777A (en) * 1999-04-28 2000-11-14 3M Innovative Properties Company Single station continuous log roll winder
US6196492B1 (en) * 1998-01-28 2001-03-06 Voith Sulzer Papiertechnik Patent Gmbh Roll winder and process of operating same
US6290164B1 (en) 2000-03-01 2001-09-18 Kt Equipment (International) Inc. Method and apparatus for supplying strip material
US6536702B1 (en) 1998-06-10 2003-03-25 The Goodyear Tire And Rubber Company Surface winding on an a-frame winder
US6641080B2 (en) * 2001-12-28 2003-11-04 Kimberly-Clark Worldwide, Inc. Method and apparatus for winding a web
US6739544B2 (en) 2001-03-29 2004-05-25 Sumitomo Heavy Industries, Ltd. Winding roll presser device and long material winding method
US6820834B1 (en) 1998-04-24 2004-11-23 Metso Paper, Inc. Reel up
US6866213B2 (en) 2001-12-28 2005-03-15 Kimberely-Clark, Worldwide, Inc. Rolled web products having a web wound in an oscillating fashion
US6869039B2 (en) 1999-01-22 2005-03-22 Metso Paper, Inc. Method and apparatus for winding a paper web
US6951676B2 (en) 2000-09-25 2005-10-04 3M Innovative Properties Company Butt splicing tapes and butt splicing methods
US7011005B2 (en) 2001-05-14 2006-03-14 Metso Paper, Inc. Method for positioning the slitters of a slitter-winder in a paper or board machine
US20060175456A1 (en) * 2003-06-17 2006-08-10 Ilkka Naatti Method in reeling up and a reel-up
US20070023561A1 (en) * 2005-07-08 2007-02-01 Matti Kemppainen Method in a Belt Reeler and a Belt Reeler
US20080006730A1 (en) * 2004-06-30 2008-01-10 Metso Paper, Inc. Method and an Apparatus for Controlling a Nip Profile of a Reeling Nip
DE202008009696U1 (de) 2007-08-15 2008-09-11 Metso Paper, Inc. Gurtwalzenwerk
US20090166465A1 (en) * 2004-06-30 2009-07-02 Metso Paper, Inc. Method in a Reel-Up and a Reel-Up
US20090189008A1 (en) * 2004-10-11 2009-07-30 Metso Paper, Inc. Reel-Up and Also a Method and Measuring Unit in Such a Reel-Up
DE202011005357U1 (de) 2010-04-27 2011-10-20 Metso Paper, Inc. Teilbahnwickler
WO2020117492A1 (en) * 2018-12-06 2020-06-11 Paper Converting Machine Company Method of initiating a web winding process in a web winding system

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FI81770C (fi) * 1987-05-20 1990-12-10 Valmet Paper Machinery Inc Foerfarande vid styrning av pappers rullstol.
GB2210068B (en) * 1987-09-25 1992-01-08 Plessey Co Plc Linear drive apparatus
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DE4201815A1 (de) * 1992-01-24 1993-07-29 Jagenberg Ag Verfahren und maschine zum aufwickeln einer papier- oder kartonbahn
DE4208790C2 (de) * 1992-03-19 1994-10-20 Voith Gmbh J M Tragwalzen-Wickeleinrichtung
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DE4427877C1 (de) 1994-08-06 1996-03-14 Kleinewefers Gmbh Wickelvorrichtung mit einer Wickelrolle für bahnförmiges Material
DE19729375A1 (de) 1997-07-09 1999-01-14 Ltg Lufttechnische Gmbh Vorrichtung zum Befestigen einer biegsamen Platte auf dem Umfang des Zylinders einer Lackiermaschine
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DE2908294A1 (de) * 1979-03-03 1980-09-04 Voith Gmbh J M Vorrichtung zum aufwickeln von bahnfoermigem gut, z.b. von papier
US4465243A (en) * 1981-05-27 1984-08-14 Jagenberg Ag Method for the shaftless winding of a web

Cited By (42)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5209418A (en) * 1985-04-24 1993-05-11 Alexander Machinery, Inc. Web unwinding apparatus and method
US4927091A (en) * 1987-04-29 1990-05-22 Jagenberg Aktiengesellschaft Device for winding and unwinding a web of material
US4921183A (en) * 1987-05-20 1990-05-01 Valmet Paper Machinery Inc. Method and device for the reeling of a web
US4842209A (en) * 1987-05-20 1989-06-27 Valmet Paper Machinery Inc. Method and device in the winding of a web
US4901935A (en) * 1987-05-27 1990-02-20 Ferag Ag Apparatus for unwinding printed products wound in conjunction with a winding band in imbricated formation upon a winding core
US5067871A (en) * 1988-07-18 1991-11-26 Kone Oy Procedure for horizontal storage of paper rolls
US5022597A (en) * 1989-09-27 1991-06-11 Krantz America, Inc. Sheet winding apparatus
US5257748A (en) * 1989-09-27 1993-11-02 Krantz America, Inc. Sheet winding apparatus
US5167376A (en) * 1989-12-07 1992-12-01 G.D. Societa' Per Azioni Device for removing adhesive tape from a reel of strip material
US5150850A (en) * 1991-05-10 1992-09-29 Beloit Corporation Method for winding a traveling web on a belted two drum wound web roll winder
US5961065A (en) * 1994-05-26 1999-10-05 Valmet Corporation Method in winding of a web
US5732902A (en) * 1994-05-26 1998-03-31 Valmet Corporation Method and device in winding of a web
US5918830A (en) * 1997-02-13 1999-07-06 Valmet Corporation Reeling device and method in reeling of a paper web or equivalent
US5938144A (en) * 1997-06-25 1999-08-17 Voith Sulzer Papiermaschinen Gmbh Winding machine
WO1999001363A1 (en) * 1997-07-03 1999-01-14 Valmet-Karlstad Ab Apparatus and method for winding paper
CN1092597C (zh) * 1997-07-03 2002-10-16 梅特索·佩珀·卡尔斯塔德公司 卷纸装置及方法
US6012673A (en) * 1997-08-12 2000-01-11 Voith Sulzer Finishing Gmbh Winding device and method
WO1999035070A1 (en) * 1997-12-22 1999-07-15 Valmet Corporation Pressure roller reel-up
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Also Published As

Publication number Publication date
AT399855B (de) 1995-08-25
DE3639244C2 (de) 1998-06-04
SE8604788L (sv) 1987-05-21
FR2590244B1 (fr) 1989-03-31
FI74260B (fi) 1987-09-30
JPH0694319B2 (ja) 1994-11-24
GB2183223A (en) 1987-06-03
NO162226C (no) 1989-11-29
NO864626L (no) 1987-05-21
NO864626D0 (no) 1986-11-19
ATA309086A (de) 1994-12-15
SE461585B (sv) 1990-03-05
FI854571A (fi) 1987-05-21
FI74260C (fi) 1988-01-11
SE8604788D0 (sv) 1986-11-07
JPS62130949A (ja) 1987-06-13
GB8627492D0 (en) 1986-12-17
AU581351B2 (en) 1989-02-16
FR2590244A1 (fr) 1987-05-22
FI854571A0 (fi) 1985-11-20
AU6553486A (en) 1987-05-28
GB2183223B (en) 1989-10-04
NO162226B (no) 1989-08-21
CA1264048A (en) 1989-12-27
DE3639244A1 (de) 1987-05-21

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